Independent control means for fluid pressure device

ABSTRACT

An independent control means to govern the operation of a fluid pressure device having a stator element and a rotor element constituting a stator-rotor mechanism, in which the stator element has a fixed axis and in which the rotor element has a movable axis with said rotor element having a rotational movement about its own axis and an orbital movement about the fixed axis. The entrance of fluid to the stator-rotor mechanism and the exit of fluid from the stator-rotor mechanism is governed by a rotary valve in the fluid pressure device. The independent control means features an actuating means for rotating the rotary valve independently of the rotor element by which the rotary valve is usually driven. The independent control means also features a by-pass valve which, when operated, fluidly interconnects the inlet and outlet ports of the fluid pressure device, whereby the rotor element may be stopped instantly.

United States Patent [191 Woodling [54] INDEPENDENT CONTROL MEANS FOR FLUID PRESSURE DEVICE [76] Inventor: George V. Woodling, 22077 West Lake Road, Rocky River, Ohio 221 Filed: July 11, 1968 211 Appl. No.:. 744,135

52 u.s.cl ..4l8/61 [51] 1111.01. ..F0lc 1/10, F040 1/06 [58] FieldofSearch ..9l/56,96,58,81,459,470, 91/35; 60/525; l37/624.l3; 103/130; 418/61 [56] References Cited v UNITED STATES PATENTS 2,138,050 11 1938 Vickers ..9l/87 Primary Examiner-Martin P. Schwadron Assistant Examinerlrwin C. Cohen Attorney-Woodling, Krost, Granger and Rust [57] ABSTRACT An independent control means to govern the operation of a fluid pressure device having a stator element and a rotor element constituting a stator-rotor mechanism, in which the stator element has a fixed axis and in which the rotor element has a movable axis with said rotor element having a rotational movement about its own axis and an orbital movement about the fixed axis. The entrance of fluid to the stator-rotor mechanism and the exit of fluid from the stator-rotor mechanism is governed by a rotary valve in the fluid pressure device.

The independent control means features an actuating means for rotating the rotary valve independently of the rotor, element by which the rotary valve is usually driven. The independent control means also features a by-pass valve which, when operated, fluidly interconnects the inlet and outlet ports of the fluid pressure device, whereby the rotor element may be'stopped instantly.

10 Claims, 7 Drawing Figures 7 PATENTED FEB] 3I973 SHEET 10F 2 INVENTOR.

GEORGE V WOODLING PATENTED-FEB 13 ms SHEET 2 OF 2 SUPPLY SOURCE FIG.7

BY- PAS S VALVE INVENTOR.

. GEORGE V. WOODLING WM W INDEPENDENT CONTROL MEANS FOR FLUID PRESSURE DEVICE This application is an improvement in my pending applications,- Ser. No, 637,382 filed May 10, 1967, now US. Pat. No. 3,405,603; Ser. No. 684,705, filed Nov. 21, 1967, now abandoned; and Ser. No. 715,247 filed Mar. 22, 1968, now U.S. Pat. No. 3,536,225.

An object of my invention is the provision of independent control means for controlling the speed of rotation and the instant stoppage of the rotor element.

Another object is to drive the rotary valve of the fluid pressure device independently of the rotor element by which the rotary valve is usually driven.

Another' object is to drive the rotary valve in response to any desired operating condition.

Another object is to provide for precise stopping of the rotor element.

Another object is the provision of a by-pass valve to fluidly interconnect the inlet and outlet ports of the fluid pressure device for precisely stopping the rotor element.

Another object is the provision of independent actuating means for rotating the rotary valve.

Another object is to provide for controlling the operation of the independent actuating means and the by-pass valve substantially simultaneously.

Other objects and a fuller understanding of this invention may be had by referring to the following description and claims, taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a side view of a fluid pressure device, in which my invention may be incorporated, partly shown in vertical section to illustrate the rotary valve for controlling the entrance of fluid to and the exit of fluid from the stator-rotor mechanism, the section through the rotary valve being taken along the line l--1 of FIG.

FIG. 2 is a view taken along the line 2-2 of FIG. 1, under the end cap, showing the stator-rotor mechanism;

FIG. 3 is a view taken along the line 3--3 of FIG. 1, with the rotary valve being omitted, the view being principally a right-hand end view of the hollow housing showing the fluid ports and the bearing support means for the rotary valve, including a cross-section of the actuating shaft;

FIG. 4 is a view taken along the line 3-3 of FIG. 1, but looking in a direction opposite from that indicated by the arrows and showing the side of the stationary valve member against which the rotary valve sealingly engages;

FIG. 5 is a view taken along the line 33 of FIG. 1, showing only the rotary valve face which sealingly engages the stationary valve face of FIG. 4;

FIG. 6 is a diagrammatical view of a control system, including an electric motor and a by-pass valve, for controlling the operation of a fluid pressure device; and

FIG. 7 is a diagrammatical view of a modified control system, in which the operation of the fluid pressure device may be governed by directional steering means.

With reference to the drawings, the fluid pressure device is substantially the same as that shown and described in my above-mentioned applications and the description therein shall apply to this application with respect to common subject matter. The description in this application will be directed principally to the valve system means and the improvement of the independent control means for the rotary valve.

Briefly, the fluid pressure device comprises a main housing, 20, a main shaft 25 rotatively mounted in the housing, a stator-rotor mechanism 31 having a stator element 32 and a rotor element 33, a stationary valve member 29 and a rotary valve member 28. An end cap 34 encloses the stator-rotor mechanism. The end cap may be held by screws 35. An actuating shaft 39 drivingly interconnects the main shaft 25 to the rotor element 33. The stationary valve member 29 has face wall means including a stationary valve face 81 abutting against the end wall of the housing 20, whereby the housing and the stationary valve member constitute enclosure means for the rotary valve. The stationary valve member 29 may be secured to the end of the housing 20 by screws 30. The housing 20 is hollow from end-to-end, and intermediate the ends of the hollow housing, there is provided an internal rib 21, which generally separates the hollow housing into a left-hand end compartment in which the main shaft 25 is rotatively mounted and a right-hand end compartment in which rotary valve is rotatively mounted.

Pressed against the internal rib 21 is a bushing 22 having a right-hand stationary end face 17 disposed substantially parallel to and spaced axially from the stationary valve face 81. The rotary valve 28 is mounted between the stationary valve face 81 and the stationary end face 17 and has a rotary valve face 82 which makes a fluid sealing engagement with the stationary valve face 81 and a rotary end face 66 which makes a fluid sealing engagement with the stationary end face 17. The rotary valve 28 is mounted within a counter bore having an internal wall surface 68 surrounding and radially spaced from the rotary valve member 28 and defines therewith external (first) annular fluid chamber means which extends all the way around the rotary valve member. The external annular fluid chamber is connected in constant fluid communication with a fluid port 23 provided in the housing 20, see FIG. 3. The fluid port 23 extends through the housing wall and intersects with the internal wall surface 68, next adjacent the right-hand side of the bushing 22.

The rotary valve member 28 has a hollow shaft 13 with insideand outside surfaces. The hollow shaft 13 extends from the rotary valve member and has a bearing portion mounted with an anti-friction roller bearing unit 14. The bearing unit 14 comprises a plurality of roller bearings encompassing the bearing portion of the hollow shaft 13 and mounted within a cup 15 which is pressed into the inner surfaces of the rib 21 and the bushing 22. The hollow shaft 13 extends through, and has a terminating end portion projecting in an axial direction beyond the roller bearing unit 14 and driven by a set of bevel gears indicated by the reference character 40.

The rotary valve member 28 has a central opening defined by internal wall surface means 76. This opening, including also the opening in the hollow shaft 13, constitutes internal (second) annular fluid chamber means connected in constant fluid communication with a fluid port 24 provided in the housing 20, see FIG. 3. The fluid port 24 extends through the housing wall and intersects with an internal bore 18, next adjacent the left-hand side of the internal rib 21.

The length of the rotary valve 28 must match the axially fixed length between the stationary end face 17 of the bushing 22 and the stationary valve face 81. To this end, the rotary valve 28 is provided with built-in axial fixation means, whereby its effective length may be varied to match the axially fixed length between the stationary end face 17 and the stationary valve face 81. As shown in FIG. 1, the hollow shaft 13 of the rotary valve 28 has an external annular flange 42 connected thereto and is provided with a sealing surface constituting the rotary end face 66 in fluid sealing engagement with the stationary end face 17 of the bushing 22. The hollow shaft 13, between the stationary end face 17 and the stationary valve face 81, may be characterized as comprising an annular valve body having a terminating end portion 44 with an end face constituting an annular surface area band 43, see FIG. 5, where the band 43 is indicated by the concentric dashdot lines. The terminating end portion 44 has an external flange-rim 45 extending outwardly therefrom and an internal flangerim 46 extending inwardly therefrom. Preferably, there is a clearance 49 between the outside of the external flange-rim 45 and the internal wall surface 68, with the result the rotary valve is solely supported for rotation by the anti-friction bearing unit 14. The external flange-rim 45 separates fluid in the external (first) annular fluid chamber from the stationary valve face 81 and the internal flange-rim 46 separates fluid in the internal (second) annular fluid chamber from the stationary valve face 81. The external flange-rim 45 and the internal flange-rim 46 define a rotary face which, together with the annular surface area band 43, constitutes the rotary valve face 82. The terminating end portion 44 of the annular valve body from which the external and internal flange-rims 45 and 46 extend, may be characterized as a common intermediate annular body portion having a diameter greater than that of the hollow shaft 13. interconnecting the common intermediate annular body portion and the hollow shaft 13 is a sloping annular connecting disk 48 which may be resistingly deformable (bent) in an axial direction to fix the effective axial length of the rotary valve to match the axial distance between the stationary end face 17 and the stationary valve face 81. In assembly, the rotary valve 28 may be axially compressed until the rotary valve face 82 is flush with the end wall face of the housing and then, when the stationary valve member 29 is bolted to the end wall face of the housing, there is provided the right amount of axial fluid sealing clearance between the rotary valve face 82 and the stationary valve face 81. As the disk 48 is axially deformed in the compression operation, the rotary valve face 82 is maintained parallel to the stationary valve face 81 since the common intermediate annular body portion 44 is free to bend where it is connected to the disk 48. The axially deformable connection disk 48 constitutes a built-in axial fixation means by which the effective length of the rotary valve may be fixed by a compression operation.

In this application, the term stator" and rotor are not used in a limited sense. The term stator" is applied to the element which has a fixed axis and the term rtor" is applied to the element which has a movable axis characterized in that said rotor is disposed for rotational movement about its own movable axis and for orbital movement about said fixed axis of the stator. Thus, in this application, the outer surrounding element, usually referred to as the stator, may be either the stator or the rotor, depending upon whether it has a fixed axis or a movable axis and the inner element, usually referred to as the rotor, may be either the rotor or the stator depending upon whether it has a movable axis or a fixed axis.

In the description, my device will be described as a fluid motor, but it is understood that it may be utilized for any other related purpose, particularly a pump.

As illustrated in FIG. 2, the stator element 32 has seven internal teeth which defines the outer wall of a fluid compartment. The rotor element 33 has six external teeth, one less than that of the stator element. The stator element may be described as having (n) number of internal teeth and the rotor element may be described as having (n-I) number of external teeth. The stator element has a center 69, usually referred to as the fixed or stationary axis since the stator element is stationarily mounted and does not rotate. In this application and claims, the expression fixed stator axis" or simply fixed axis," includes not only the fixed axis of the rotor, but also any axis which coincides, or is in axial alignment therewith.

The rotor 33 has a movable axis, identified by the reference character 70, and is radially spaced from and moves in an orbital path about the fixed axis 69 of the stator. The orbital path of the movable axis 70 is a true circle with its center coinciding with the fixed axis of the stator. The diameter of the true circle, orbital path, is equal to the difference in the radial dimension between the crest contour and the root contour of a stator tooth. Upon relative movement between the rotor and the stator, the movable axis 70 of the rotor orbits in a true circle about the fixed axis of the stator. As the rotor moves within the stator, the inter-meshing teeth of the rotor and stator divide the fluid compartment confined therebetween into high and low pressure chambers along a revolving divisional line passing substantially diametrically through the fixed axis of the stator. For the position in FIG. 2, the divisional line is substantially diametrically vertical. For the position shown in FIG. 2, the divisional line may be more properly described as a divisional tapering band rather than a line and comprises substantially a slender triangle having an apex at the point where the top rotor tooth in FIG. 2 touches or contacts the arcuate surface of the stator contour and having a base defined by the distance between the sealing contact engagement on opposite sides of the bottom rotor tooth when fitting full-depth into the bottom stator tooth. To rotate the rotor 33 in a clockwise direction, the chambers on the left-hand side of the revolving divisional line or tapering band become high pressure chambers and the chambers on the right-hand side become low pressure chambers. The high and low pressure chambers, which may be referred to as operating chambers, alternately expand and contract as the rotor and stator move relative to each other. The divisional line or tapering band continually revolves in a counter-clockwise direction as the rotor rotates in a clockwise direction within the stator.

As shown in FIG. 1, the actuating shaft 39 has a right-hand end portion provided with male spline teeth system 53. In the de-energized condition of the control system 53 with the switch 58 open, the spool 55 isin a downward position, which fluidly inter-connects the fluid ports 23 and 24 of the fluid pressure device through an annular groove 61 in registration with the illustrated ports 64 and 65 in the casing 56 of the by-pass valve. As a result of the fluid inter-connection, the fluid from the pump 59 is directly by-passed to the sump 60.

' Under this condition, the fluid is dis-continued from flowing through the fluid pressure device.

In operation of FIG. 6, the closing of the switch 58 energizes the control system 53, which, in turn, energizes the motor 51 and the solenoid 57. The instant that the solenoid is energized, the spool 57 is actuated to its upward position, whereupon the annular groove 61 is moved out-of-registration with the ports 64 and 65, thereby enabling the fluid pump 59 to deliver pressurized fluid to the fluid pressure device for operating same. The instant that the electric motor is energized, it starts to rotate the set of bevel gears 40 for driving the rotary valve. The speed of rotation of the rotary valve determines the speed of rotation of the rotor element 33, assuming that substantially constant fluid pressure is delivered to the fluid pressure device. Thus, in FIG. 6, the speed of the rotor element 33 may be governed by the setting of the control knob 50 of the control system 53. To stop the rotation of the rotor element 33, it is only necessary to open the switch 58. Instantly, the fluid by-pass valve 54, fluidly inter-connects the fluid ports 23 and 24 of the fluid pressure device; whereupon, through the loss of fluid pressure, the rotor element 33 stops rotating substantially immediately. Also, the rotation of the rotary valve 28 is stopped substantially immediately.

In FIG. 7, the fluid pressure device is governed by a directional steering means operated by a steering wheel 97, which may be mechanically connected to the output shaft of the fluid pressure device and to the shaft 52 which drives the set of bevel gears 40. The mechanical connection is illustrated by the dash-dot lines 98 and 99. As the shaft 52 is rotated by the steering wheel 97, the rotor element 33 is accordingly operated to drive the output shaft of the fluid pressure device for transmitting a power movement to guide the wheels 100 and 101 of the vehicle. In the event of failure of the fluid pressure device to operate, the wheels 100 and 101 may still be operated by the steering wheel 97 through the mechanical connection indicated by the dash-dot line 98. When the steering wheel is in a neutral or center position, the annular groove 61 of the by-pass valve 54 is in registration with the two ports 64 and 65. The rotation of the rotor element 33 is thus arrested for loss of fluid pressure. The instant that the steering wheel 97 is turned either clockwise or counterclockwise, the mechanical connection indicated by the dash-dot line 102 is such that the annular groove 61 is moved out-of-registration with the ports 64 and 65,

whereupon pressurized fluid is delivered to the fluid pressure device for transmitting a power movement to guide the wheels 100 and 101 in accordance with the position of the steering wheel 97. Thus, in FIG. 7, the wheels 100 and 101 are power operated to a position related to the position of the steering wheel 97. The instant that the steering wheel is re-turned to neutral, the groove 61 is again brought into registration with the ports 64 and 65, thus stopping the rotation of the rotor element 33.

In FIGS. 6 and 7, the by-pass valve 54 is external of the fluid pressure device and may be readily inspected and replaced, if necessary, without disturbing the fluid pressure device. The actuation of the rotary valve by the set of bevel gears 40 simplifies the operation of the fluid pressure device, as well as enabling the speed of the rotor element 31 to be controlled by a movement externally of the fluid pressure device. In addition, the speed of the rotor element 33 may be governed without resorting to a fluid pump having variable pressure and variable volume to change the speed. The fluid pump 59 may be of a constant volume and of a constant pressure. This greatly simplifies the operation of the fluid pressure device. In FIG. 6, the control system 53 may be made responsive to the speed of the output shaft through responsive means indicated by the dash-dot line 103, whereby the speed of the rotary valve and that of the output shaft may be held substantially in synchronism. The shaft 52 that operates the set of bevel gears 40 may be actuated by means, other than that shown, in accordance with the movements of any desired condition.

Although this invention has been described in its preferred form with a certain degree of particularity, it is understood that the present disclosure of the preferred form has been made only by way of example and that numerous changes in the details of construction and the combination and arrangement of parts may be resorted to without departing from the spirit and the scope of the invention as hereinafter claimed.

What is claimed is:

1. In a fluid pressure device having stator and rotor means constituting fluid pressure operating means, said stator means having a fixed axis, said rotor means having a movable axis, said rotor means having a rotational movement about its own movable axis and an orbital movement about said fixed axis, valve system means including rotary valve means free from mechanical rotational connection with said rotor means, and actuating means having source movement means independent of the rotational movement of said rotor means to rotate said rotary valve means for controlling the entrance of fluid to and the exit of fluid from said fluid pressure operating means, said actuating means including an actuating shaft rotatably disposed substantially perpendicular to the axis about which said rotary valve means rotates, and gear means interconnecting said actuating shaft and said rotary valve means, said rotary valve means having a rotary valve face including a circumferential surface area band having outer and inner circumferences respectively defined by two concentric circles, said outer and inner circumferences having a medium circumference therebetween, said fluid controlled by said rotary valve means flowing in one direction through said rotary valve face outwardly of said median circumference and flowing in the opposite direction through said rotary valve face inwardly of said medium circumference.

2. The structure of claim 1, having housing means within which said rotary valve means is mounted, said actuating means extending through said housing means with said source movement means disposed externally of said housing means.

71 which fit within female spline teeth 72 in the rotor, being referred to herein as first connection means. Thus, the right-hand end portion of the actuating shaft 39 is disposed for rotational movement about its own movable axis and for orbital movement about the fixed axis of the stator. The connection means between the left-hand end portion of the actuating shaft 39 and the main shaft 25, herein referred to as second connection means, also comprises male spline teeth 73 on the actuating shaft 39 which fit within female spline teeth 74 in the central core of the main shaft 25. The left-hand end portion of the actuating shaft, that is the second connection means, is disposed for rotational movement substantially free from orbital movement about the fixed axis of the stator.

The valve system means in the present application, comprising the rotary valve member 28 and the stationary valve member 29, operates substantially the same as that shown and described in my above mentioned applications. To this end, the external flange-rim 45 has a first series of six commutating fluid connection means 83 extending therethrough and connects the external (first) annular fluid chamber means, outside of the rotary valve, in constant fluid communication with the stationary valve face 81. The internal flange-rim 46 has a second series of six commutating fluid connection means 84 extending therethrough and connects the internal (second) annular fluid chamber means, inside the rotary valve, in constant fluid communication with the stationary valve face 81. The annular surface area band 43 is disposed between and sealingly separates the first and second series of commutating fluid connection means 83 and 84. It will also be seen that the common intermediate annular body portion 44 separates the first and second series of commutating fluid connection means 83 and 84. The first and second series of commutating connection means are alternately disposed with respect to each other and are circumferentially disposed relative to the fixed axis and spaced at annular intervals thereabout at substantially 30 from each other. The stationary valve member 29 has seven fluid openings 80 communicating respectively with the operating fluid chambers in the stator-rotor mechanism. The seven fluid openings 80 in the stationary valve member 29 terminate respectively in the stationary valve face 81, with the fluid opening being circumferentially disposed about the fixed axis and spaced at annular intervals thereabout at 51 3/7 from each other.

In operation as a fluid motor, high pressure fluid from the high pressure port 23 commutatively flow through the first series of commutating fluid connection means 83 of the rotary valve into the fluid openings 80 of the stationary valve member 29 and thence into the expanding pressure fluid chambers in the stator-rotor mechanism and drives the rotor 33 in a clockwise rotational direction within the stator 32. As the rotor is driven, the exhaust fluid in the low pressure contracting chambers commutatively flows through the fluid openings 80 of the stationary valve 29 into the second series of fluid commutating connection means 84 of the rotary valve and thence to the low pressure port 24. As the rotor is driven by the high pressure fluid, it operates the main shaft 25 through the actuating shaft 39. The registration of the fluid connection means provided by the rotating valve face 82 in sealing engagement with the stationary valve face 81 is such that there is a first series of commutating fluid connections between the high pressure port 23 and the expanding fluid chambers in the stator-rotor mechanism and a second series of commutating fluid connections between the contracting fluid chambers and the low pressure port 24. In FIG. 4, the place where the annular surface area band 43 rotates against the stationary valve face 81, is illustrated by the concentric dash-dot lines being the same as the dash-dot lines in FIG. 5. Thus, the terminal openings have an outer portion and an inner portion 91 respectively residing outsideand inside the place where the annular surface area band 43 rotates against the stationary valve face 81. As will be seen, the outer portion 90 and the external (first) annular fluid chamber, outside of the rotary valve, are commutatively connected together, and the inner portion 91 and the internal (second) annular fluid chamber, inside of the rotary valve, are commutatively connected together. In this construction, the terminal openings 80 have an elongated dimension in a radial direction extending across the annular band 43, whereby fluid may commutatively flow through both the first and second series of fluid connection means 83 and 84. The elongated dimension of the terminal openings 80 are such that they radially overlap the first and second series of fluid connection means 83 and 84 during commutation movement.

The rotating valve 28 is independent of any radial thrust or of any end thrust to which the main shaft 25 may be subjected. Also, the rotating valve 28 is substantially free from any radial thrust or any end thrust due to fluid pressure acting thereupon. In summary, the valve system means, including the rotary valve 28 and the stationary valve member 29, controls the entrance of fluid to and the exit of fluid from the operating chambers of the stator-rotor mechanism.

The rotary valve 28 is free from mechanical rotational connection with the rotor element 33 and is independently operated by the control means illustrated in FIGS. 6 and 7 instead of by the rotor element 33, which is usually employed to drive the rotary valve. In FIG. 6, the set of bevel gears, indicated by the reference character 40, is driven by an electric motor 51 through a shaft 52 extending through the housing 20 of the fluid pressure device. The shaft 52, where it passes through the housing 20, is provided with the usual shaft seal which, for drawing purposes, is not shown. Through a program control system, indicated by the reference character 53, the motor 51 may operate in either direction for driving the rotary valve in a clockwise direction or in a counter-clockwise direction. The speed of the electric motor 51 may be governed by a control knob 50 in the program control system 53. Pressurized fluid may be delivered to the inlet port 23 by means of a fluid pump 59. The exhaust fluid from the outlet port 24 may be delivered to a sump 60. As illustrated in FIG. 6, the program control system 53 is disposed to operate a by-pass fluid valve 54 which provides for instant stoppage of the rotor element 33. The by-pass fluid valve 54 may comprise a valve spool 55 which may be slidably mounted in a valve casing 56. The spool 55 may be actuated up and down by means of a solenoid 57 governed by the program control 3. The structure of claim 2, wherein said source movement means includes power motor means.

4. The structure of claim 3, wherein said power motor means comprises an electric motor.

5. The structure of claim 2, wherein said source movement means includes directional steering means.

6. In a fluid pressure device having fluid pressure operating means disposed to have a rotational and orbital operating movement, valve system means including stationary valve'means and rotary valve means, said rotary valve means having first and second end portions, said first end portion sealingly engaging said stationary valve means for controlling the entrance of fluid to and the exit of fluid from said fluid pressure operating means, said second end portion including a hollow shaft, bearing support means having first and second sides, said bearing support means rotatively supporting said hollow shaft with said first end portion of said rotary valve means disposed on said second said of said bearing support means, and actuating means having an actuating movement independent of said operating movement for engaging said hollow shaft from said first side of said bearing support means for driving said rotary valve means, said actuating means including an actuating shaft rotatably disposed substantially perpendicular to the axis about which said rotary valve means rotates, and gear means interconnecting said actuating shaft and said rotary valve means, said rotary valve means having a rotary valve face including a circumferential surface area band having outer and inner circumferences respectively defined by two concentric circles, said outer and inner circumferences having a median circumference therebetween, said fluid controlled by said rotary valve means flowing in one direction through said rotary valve face outwardly of said median circumference and flowing in the opposite direction through said rotary valve face inwardly of said median circumference.

7. The structure of claim 6, having housing means within which said bearing support means and said rotary valve means are mounted.

8. The structure of claim 7, wherein said actuating means includes source movement means disposed externally of said housing means.

9. The structure of claim 8, wherein said source movement means includes an electric motor.

10. The structure of claim 8, wherein said source movement means includes directional steering means. 

1. In a fluid pressure device having stator and rotor means constituting fluid pressure operating means, said stator means having a fixed axis, said rotor means having a movable axis, said rotor means having a rotational movement about its own movable axis and an orbital movement about said fixed axis, valve system means including rotary valve means free from mechanical rotational connection with said rotor means, and actuating means having source movement means independent of the rotational movement of said rotor means to rotate said rotary valve means for controlling the entrance of fluid to and the exit of fluid fRom said fluid pressure operating means, said actuating means including an actuating shaft rotatably disposed substantially perpendicular to the axis about which said rotary valve means rotates, and gear means interconnecting said actuating shaft and said rotary valve means, said rotary valve means having a rotary valve face including a circumferential surface area band having outer and inner circumferences respectively defined by two concentric circles, said outer and inner circumferences having a medium circumference therebetween, said fluid controlled by said rotary valve means flowing in one direction through said rotary valve face outwardly of said median circumference and flowing in the opposite direction through said rotary valve face inwardly of said medium circumference.
 1. In a fluid pressure device having stator and rotor means constituting fluid pressure operating means, said stator means having a fixed axis, said rotor means having a movable axis, said rotor means having a rotational movement about its own movable axis and an orbital movement about said fixed axis, valve system means including rotary valve means free from mechanical rotational connection with said rotor means, and actuating means having source movement means independent of the rotational movement of said rotor means to rotate said rotary valve means for controlling the entrance of fluid to and the exit of fluid fRom said fluid pressure operating means, said actuating means including an actuating shaft rotatably disposed substantially perpendicular to the axis about which said rotary valve means rotates, and gear means interconnecting said actuating shaft and said rotary valve means, said rotary valve means having a rotary valve face including a circumferential surface area band having outer and inner circumferences respectively defined by two concentric circles, said outer and inner circumferences having a medium circumference therebetween, said fluid controlled by said rotary valve means flowing in one direction through said rotary valve face outwardly of said median circumference and flowing in the opposite direction through said rotary valve face inwardly of said medium circumference.
 2. The structure of claim 1, having housing means within which said rotary valve means is mounted, said actuating means extending through said housing means with said source movement means disposed externally of said housing means.
 3. The structure of claim 2, wherein said source movement means includes power motor means.
 4. The structure of claim 3, wherein said power motor means comprises an electric motor.
 5. The structure of claim 2, wherein said source movement means includes directional steering means.
 6. In a fluid pressure device having fluid pressure operating means disposed to have a rotational and orbital operating movement, valve system means including stationary valve means and rotary valve means, said rotary valve means having first and second end portions, said first end portion sealingly engaging said stationary valve means for controlling the entrance of fluid to and the exit of fluid from said fluid pressure operating means, said second end portion including a hollow shaft, bearing support means having first and second sides, said bearing support means rotatively supporting said hollow shaft with said first end portion of said rotary valve means disposed on said second said of said bearing support means, and actuating means having an actuating movement independent of said operating movement for engaging said hollow shaft from said first side of said bearing support means for driving said rotary valve means, said actuating means including an actuating shaft rotatably disposed substantially perpendicular to the axis about which said rotary valve means rotates, and gear means interconnecting said actuating shaft and said rotary valve means, said rotary valve means having a rotary valve face including a circumferential surface area band having outer and inner circumferences respectively defined by two concentric circles, said outer and inner circumferences having a median circumference therebetween, said fluid controlled by said rotary valve means flowing in one direction through said rotary valve face outwardly of said median circumference and flowing in the opposite direction through said rotary valve face inwardly of said median circumference.
 7. The structure of claim 6, having housing means within which said bearing support means and said rotary valve means are mounted.
 8. The structure of claim 7, wherein said actuating means includes source movement means disposed externally of said housing means.
 9. The structure of claim 8, wherein said source movement means includes an electric motor. 